Cutoff machine



Dec. 14, 1943. R. E. PIERCE CUTOFF MACHINE Filed Oct. '2, 1942 5Sheets-Sheet i R. E. PIERCE CU'I'OFF MACHINE Dec. 14, 1943.

Filed Oct. 2, 1942 5' Sheets-Sheet 2 'Dec. 14, 1942..

- R. 5:. PIERCE CUTOFF MACHINE Filed 001:. 2. 1942 5 Sheets-Sheet 5 Dec.14, 1943.

) R. E. PIERCE 2,336,957

CU'I'OFF MACHINE Filed Odt. 2, 1942 5 Sheets-Sheet 4 Patented Dec. 14,1943 UNETED STATES PATENT OFFECE CU'EOFF MACHINE Robert E. Pierce, LosAngeles, Calif., assignor' to Bemis Bro. Bag Company, St. Louis, Mo., acorporation of Missouri 13 Claims This invention relates to cut-01fmachines, and with regard to certain more specific features, to cut-offmachines for several moving webs.

Among the several objects of the invention may be noted the provision ofa web cut-off machine which is particularly useful for cutting intosections multi-wall tubing such as is used for paper bags, which machineeffects cut-off by an action eliminating substantially all longitudinaltearing, thereby providing a neat and smooth separating cut, whetherstraight or angular, with all edges of any multi-Wall material flush;the provision of apparatus of the class described which effects cuttingby a simple mechanism which is always operative at equal time intervalsbut which is equally effective for all Web segment lengths as determinedby any of the necessarily various speeds of passage of webbing throughthe machine; and the provision of a machine of the class described whichintroduces relatively few additional structural parts or complexities ofoperation over those required for conventional cut-off machines. Otherobjects will be in part obvious and in part pointed out hereinafter.

The invention accordingly comprises the elements and combinations ofelements, features of construction, and arrangements of parts which willbe exemplified in the structures hereinafter described, and the scope ofthe application of which will be indicated in the following claims.

In the accompanying drawings, in which is illustrated one of variouspossible embodiments of the invention,

Fig. 1 is a top plan view of apparatus embodying the invention;

Fig. 2 is a vertical section taken on line 2-2 of Fig. 1;

Fig. 3 is a right-side elevation of Fig. 1;

Fig. 4 is a Vertical section taken on line 4-4 of Fig. 1;

Fig. 5 is a fragmentary enlarged vertical section of a pair of cutterelements shown in position about to commence a cut;

Fig. 6 is a view similar to Fig. 5 showing the completion of a cuttingaction and start of a stripping action;

Fig. 7 is an enlarged detailed section taken on line 'l-'! of Fig. 1;

Fig. 8 is a fragmentary bottom plan view of Fig. '7;

Fig. 9 is a, diagrammatic bottom plan view of a straight upper blade andcutter bar, being viewed from line 9-9 of Fig. 2; t

Fig. 10 is a diagrammatic top plan view of a straight lower cutterrecess member (adapted to cooperate with the blade shown in Fig. 9) andbeing viewed from line Ill-40 of Fig. 2;

Fig. 11 is a view similar to Fig. 9, but showing an alternative form ofblade, and being viewed from line ll-II of Fig. 2;

Fig. 12 is a view similar to Fig. 10 but showing the recess arrangementfor cooperating with the blade arrangement of Fig. 11, being viewed fromline l2l2 of Fig. 2;

Fig. 13 is a diagrammatic plan view of multiwall tubing indicatingthereon the arrangements of alternate cuts performed by the presentmachine; and,

Figs. 14 and 15 are respectively vertical detail sections on linesl4--l4 and l5-l5 of Fig. 1.

Similar reference characters indicate corresponding parts throughout theseveral views of the drawings.

It has heretofore been the practice to cut tubing, particularlymulti-ply paper tubing for paper bags and the like, into desired lengthsby means of a pair of cooperating rotary cutters. Such cutters would beless troublesome than they are if only one predetermined length oftubing segments were to be cut on a given machine, because then the rateof advance of the cutter while cutting could be made equal to the rateof advance of the tubing web through the machine. As a practical matterit is important that a given cutting machine be adapted to successfullycut web segments to various lengths for making varions bag sizes.

Heretofore it has not been feasible in a simple machine to make theseparating cut without introducing an endwise tearing action. In thecase of single-ply tubing this tearing action produces a ragged edge,and in the case of multitubing it, in addition, causes an undesirablesteplike relationship between the edges of the various plies. Theresults are particularly undesirable in the cases where any part of thecut is longitudinal of the finished bag, as in the case of the angularcut necessary for making the end of a valved bag.

The present invention solves the above difiiculties by means of amechanism adapted to provide a laterally smooth and even cut (eitherstraight or angular) on multi-ply tubing, which cut is accurate andflush throughout the plies, regardless of the length of tubing segmentsfor which the machine is set.

Referring now more particularly to Fig. 1, there is shown at numeral I aweb of multi-ply paper tubing. The individual plies are not shown be- InFig. 13 is shown how the tubing is to be out up to form tubing segmentsfrom which paper bags are to be made. Numerals 3 indicate straightlateral cuts for forming the bottom edges of the bags, and numeral 5indicates in general an angu lar cut from which the tops of the bags areto be made, such cuts involving off-set portions I from which,respectively, the inlet valve of each bag is made. The loose rectangularpaper strip 910etween theseofi-sets I is to be removed from each cut 5.How the bags are formed fromthis point on is of no moment to the presentinvention, and there are various known ways of performing the finishingoperation. It sufiices to say that the blanks between cuts 3 and I arethe intermediate product made by the present machine, the raw materialupon whichthe machine works being the continuous web of tubing.

Referring-to Figs. 1-4, numeral II indicates the frame of the machine.Adjacent to the frame H is amotor I3which, through a belt drive I 5,drives a pulley II on a drive shaft I9. This drive shaft I9 extendsstraight'through an epicyclic gear box 2| and-near a bearing'23 in-theframe II carries a driving pinion gear 25., This pinion'gear meshes witha larger gearrZI. Gear 2'! and a concentric lower herringbone gear 29"are keyed toalower shaft 3| passing through bearing 33 in frame II. Theherringbonegear 29 meshes with an upper herringbone gear 35 ofequalnumber of teeth, .the'latter being carried upon a shaft 31which'passes through bearings 39 in the frame I I. By means of thestated gear train the shafts 3i and 31 are caused by the motor I3 torotate in the opposite directions shown in Figs. 2 and 3. Theseshafts 3|and 31 carry certain reels for supporting cutting elements, and will bedescribed hereinafter.

' Within the epicyclic gear box 2! is an adjustable take-.ofi drivewhich consists'in a driving gear i'I'keyed to the shaft I9. This gear 4|meshes with intermediate gears it rotary on studs'45, and the latterbeingcarried epicyclically upon studs .on the side of a rotary wormwheel member 41; The angular position of the worm wheel 41 may beadjusted from a meshing worm carried on a shaft 5i. Shaft 5I is undercontrol ofaniexterior crank 53 for adjustment purposes. r r

The intermediate gears t3 alsomesh with an internalgear 55 which isbolted to a carrier spider 51. The spider 51 is keyed to a quill 59which passes out of the gear box ZI and externallyhas attached to it apinion SI. The quill 59 is rotary V on' shaft I9.

From the above it will be seen that power pinion H, through intermediategears 23, will rotate the internal gear 55, and thus the spider 51 alongwith the quill 55. Thisrotates the pinion SIwith respect to the shaftis. When it is desired to change the rotary phase relationship of thegear 6| with respect to the gear 25, this may be .done'by rotating thehandle 53. Rotation of the handle 53 re-orients the intermediate gears43 by rotating their stud supports .5, and during the re-orientationangularly sets the gear 55 either backward or forward. This involvesepicyclic action of the gears 43 around gear ii. -The adjustment may bemade either while the machine is stationary or in motion; The purpose ofthe adjustment will appear.

The pinion 6| meshes with an idler 63 (Figs. 1 and 4) which in turnmeshes with a pinion 65. The latter is keyed to a shaft GI which passesthrough bearings in both sides of the frame II to the opposite side ofthe machine (Figs. 1 and 3). Here the shaft 8? carries a change gear 69.In conjunction therewith is also a rotary support for a gear sectorplate I I. The plate H has slots I3 for locking cooperation with lookingstuds 15 and also carries a rotary change gear II. The change gear I?meshes with a gear ii on a lower cross-shaft 8! carried in the frame II. Inside of the frame II the shaft carries a gear 83 and also two lowerdraw rollers 85 which are adjustable longitudinally for accommodation tovarious web widths. The gear 83 meshes with an idler B'Iwhich in turnmeshes with a gear 89 on another lower cross-shaft QI, also carried inthe frame II. The cross-shaft BI carries another pair of lower drawrollers 93 which, as in the case of the rollers 85, are adjustablelongitudinally.

Thegears 83 and 89 respectively mesh with gears 95 and 91 carried uponupper cross-shafts SB'and IE3! respectively. The shafts 99 and ISI arealso supported in the frame I I. These shafts 99 and NH respectivelycarry upper draw rollers I 03-and IH5,-adjustable longitudinally foraccommodation to various web 'widths. From the above it will be seenthatthe draw rollers 85, 93, lfitand I85 a-re'diven in the directionsindicated to draw the web of paper I into the machine. In order to ejectthe segmented web from the machine, resilient upper delivery rollersIti'i are mounted adjustably upon a cross-shaft I09 having a rotarysupport in the frame I I. This crossshaft I99 carries a sprocket II!which has a 1:1 ratio chain drive connection H3 with a sprocketII5'carried on the shaft 89. The upper delivery rollers I01cooperate-with a solid lower metal delivery roller I II, the latterbeing located upon a shaft I 59 carried in bearings in the frame II.Outsideof the frame II the shafts I539 and H9 are geared by means ofgears I2I in a 1:1 ratio. The peripheral speeds of all of the rollers93, 85, I03, I85, I61 and III are the same and in a direction to carrythe web I through the machine between shafts 3i and 37.

Each of the shafts Hand 3! carries what will hereinafter be referred toas a reel, the upper reel being indexed in the aggregate as 523 andthe'lower one as I25. Each reel has a central trunk IZ-I keyed to itsrespective shaft and each has a pair of supporting flanges I29 betweenwhich are spacing pillars ISI. The general purpose of each of thesereels is to carry a pair of cutting elements, related at so that foreach revolution two cuts are made in the web I.

The pair of cutting elements on the upper reel I23 are male elements andthe pair on the lower reel I25 are female. This relationship could bereversed. The cutting elements on one side of each reel'are for thepurpose of making a straight out such as shown at 3 in Fig. 13; and thepair of cutting elements on the other and opposite side of each reel areforthe purpose of making the angular cut (with a removed central part),such as shown at I in Fig. 13.

Referring first to the upper reel I23, it carries between the plates I29oppositely located rocking shafts I33. From each shaft I33 extend twoend arms I35 and a central arm I35a, each set of three arms carrying aknife block held to the ends of the arms by bolts ISIS. The blocks aredifferently identified as I31 and I39. The difference in identificationis to distinguish these blocks from the viewpoints of the forms ofblades which they carry for making the cuts and 3. Block I39, also shownin Fig. '1, carries a single straight blade Id: (Figs. 1-9) which is setinto a groove I53 and held in place by one or more taper pins Hi5. Theseare set in tapered holes I 51. The holes Id? partially intersect thegroove Ice, as shown in Fig. 8, so that the flat sides Ids of the pins55.5 will wedgingly hold the blade MI in place upon tightening up a nutand stud combination I'ill (Fig. 7) On its longitudinal edges the blockI38 carries clamp bars I53 held down by nut and stud combinations I55.These bars I53 clamp in place looped strips of resilient material suchas rubber I51. The looped resilient strips form resilient tubularportions running parallel on opposite sides of the blade I46.

The block I31 likewise carries clamping elcments I53 and IE5 forresilient tubular portions E51; but the blade arrangement in the blockit? is different, so as to form the angled cut 1 (Figs. 11 and 13).There are a pair of long blades its and a pair of short cross blades ItI. These blades are also held in place by means of wedges such as thewedges I 35 above described but not again shown.

The supporting arms 535 and I350; are attached to and may rock with theshafts I33. To control the rocking of the shafts i223, each one carries,outside of the flanges I29, endwise rocker arms I83. On the ends of armsI63 are follower rollers N35. The rollers I65 operate in grooves I61respectively in stationary cams H59 affixed to the frame 5 i (see, forexample, the holding studs lit in Fig. 3). The grooves or races it? inthe oppositely located cams its are the same in out line and in phaserelationship, so that the oppositely located rollers I65 associated witha given shaft I33 will in operation have equal time phases. Toe portionsI'll are oppositely located in the opposite cams. The purpose of thefollowers IE5 and cams It? is to cause the respective cutter bars I3!and I38 to move predeterminately as they approach a point of tangencywith respect to the web I for purposes the details of which will appear.

On the lower reel I like numerals designate parts like those on theupper reel. These parts consist in the central trunk I21 (carried onshaft SI), flanges I29, spacing pillars ltl, rocking shafts I33, andarms I attached to and extending from the rocking shaft I33. On therocking shafts I33 are also control arms I63 with their followers IE5.One difference in construction is that the cutter blocks I31 and I35areof female form (see grooves H5 and IiI-i respectively) forcooperation with the blades in bioclrs and I3t respectively (see Figs.9-12).

The herringbone gears 29 and 35 properly phase the motions of reels I25and 523 so that as the reels rotate, the blade B ll swings into notchI13 and the blades I53, till swing into notches I15. Resilient tubularcushions I51 are also attached to the blocks I39 and it? for resilientengagement with the cushions Iii? on the blocks I39 and I31.

The followers I535 in this lower reel I25 operate in groove it? in fixedlower cams ltd. This is indicated in Fig. 5 where the step Ill in thegroove It? is shown opposite the step Ill in the Thus while the reelsgroove I61 in the cam I59. I23 and I25 rotate oppositely, blocks I3? andare normally inward as a tangential cooperating cutting relationship isreached (compare Figs. 5 and 6). This is caused by the action of thefollowers I85 before reaching the notches Ill and I'll. During theapproach action, the opposite pairs of resilient clamps I51 engage oneanother and clamp or hold the web I ahead of and behind the region whereit is to be cut (Fig. 5). This insures that the portion I11 of the web Ihedged between the clamps I51 shall move at the same velocity as thecutting elements, during the cutting action about to occur,'regardlessof the rate at which the remainder of the web moves. The web undercertain conditions may loop somewhat in the region of approach to thecutter element, but the portion clamped between the resilient membersIt? will be unaffected and therefore be r properly cut.

Between Figs. 5 and 6, the followers I traverse the notches Ill and I1I, which has the effect of bringing the arms I35 and I35a into a moreradial position on the reels and in effect pushes the cutter blocks I31and I31 outwardly respectively with respect to the reels. This meansthat these blocks approach one another with a snap action of anessentially radial character (with respect to the web I) with acontinued peripheral component of motion tangent to the line of webmovement. This action also brings about what may be characterized as atoggle action involving the two reels on their respective centers, thearms I35 operating on their centers on the reels, and the reactions dueto the resilient strips I51 (see the center lines in Figs. 5 and 6).After cutting has been completed, the bars I31 and I31 graduallyseparate due to their peripheral motion. The groove I61 and I51 aredesigned from this point on as a gradual outwardly directed spiralaround to the notches I'll and Ill, respectively, which has the effectof again angling arms I35 forward from their radial positions andshortening the radius at which the blocks I31 and I31 move, so that uponnext approaching the web I, the blocks are again ready for the quickradial cutting movement.

From Figs. 11, 12 and 13 it will be seen that a small rectangle of papermust be removed to provide the paper valve extensions 1. In order tostripthis away from the segmental blanks which pass from the machine aneedle bar I19 is used, carrying a number of needles IBI. The needlespass loosely through openings I83 in the space between the grooves I15in block I31. This needle bar is pivotally supported on arms I85 whichare mounted upon a rocker I81 supported between extensions 58% from thearms I35. Suitable openings IilS (Fig. 2) in plates I29 allow for motionof I3? as arms ldt rock with I35. The rocker shaft I81 is rotated on itsown center by arms I853 carrying roll followers I9! which operate Withininner grooves Iii-3 of the lower cams I551. A notch 595 in each grooveI93 causes the needles Edi to rise through the block I31 at the timethat the web is cut, thus piercing the rec tangle of cut-out paperbetween the angular grooves I15 and blades I59, I6I. Then as the blocksE31 and I3? separate, this rectangular .l paper is abstracted from theblades I59, I6I and is carried around with the block I37 until theremaining spiral form of the groove I83 causes retraction of the needlesIlli so that this paper is dropped from the block as the lattertraverses the bottom of the machine. The forwardly angled positionsofthe needles I3! cause them better to pick out the waste 9 from bladesI59, Ifil. It will be clear that no corresponding needle stripperconstruction is used in association with the blocks I39 and ISEI,because there is no waste paper associated with the bottom-forming cuts3;-

In order to support and guide the web I through the machine, tables I 97and I98 are used, as shown in Fig. 2.

Operation is as'follows:

The web I is drawn into the machine by the rollers 93, I95, 95, I03 andproceeds between the reels I23 and I25. Tables I97 and I98 guide it.During movement it is caught and resiliently held between the tabs I57associated, for example, with the blocks I37 and I37. As these blocksapproach tangential cooperating cutting relationship (Fig. 5), theclamped part of the'paper hedged between the resilient strips I57 musttravel at the samerate as the blocks I37, I37, so that when, forexample,blades I59, IBI enter groove I75, there is substantially norelative 1ongitudinal motion between the blades and the paper. While theperipheral velocity of the blocks is reduced because of the rockingaction of the supporting shaft I33 caused by the followers I65 acting inthe notches HI and ill, the blocks I37 and I 37 swing into action fromthe position of Fig. 5 to that shown in Fig. 6. Cutting takes placewhile the needles I8! rise to extract the rectangular portion of paperbetween grooves I75. Hence upon separation of blocks I37 and I37, thisblock of paper is withdrawn. The'separated web segments are drawn fromthe machine by the rollers I97, H7. The-action is similar as to blocksI39, I39, except that no needle action is involved and the cut isstraight.

The length of a web segment is determined by the speed with which theweb material is fed between the reels between constantly timed periodsof cutting action, and this speed is under control of the change gears69 and 77. The larger gear 69 is, the greater is the speed. It ispreferable that for the shortest tube length desired the tangentialvelocity of the blocks 137, I37, and I39, I39, when they co-operaterespectively, shall be about equal to the web speed. This means that fora longer length of tube, the web will be passing through the machinefaster than the tangential velocity of the blocks, but this will notaffect the relative velocity of the paper at the cutting point, becausethe area I77 is clamped between the resilient members I57. Any part ofthe web that is advancing too fast toward this point merely loops uptemporarily on the table I98 and any tendency of the take-off rolls I07,H7 to pul1 these separated segments out too fastis met by slippagebetween these roll I97, H7 and these segments. All roller sets areprovided with suitable pressure controls C for controlling the pullingforce due to friction. The pressure between rolls I67 and H7 is madeenough to draw the web through without slippage in between cuttingoperations but not so much that slippage cannot take place at the rollswhen a fast moving web is gripped by clamps I57 and temporarily slowedup. This avoids tearing the web over platen I97 when cutting of it takesplace. Thus the resilient clamps I57 positively hold the paper adjacentto the blades at blade speed regardless of the various web speedsrequired for the various tube sizes. Consequently the desirable cuttingaction is the same for any length of tube being produced.

Orientation or phasing of the cuts is effected by the differentialadjustment from crank 53, whether or not the machine is in motion.

It isto be understood that Various blade shapes may be used, and ifnarrower or wider rectangular segments 9 are to be removed between theangular valve extensions '7, accordingly various numbers of holes I83 inbar I37 and needles I8I may be employed on'the bar I79.

It will be seen, by comparing Figs. 5 and 6, that the rocking cutteraction starts before the centers of the rocking shafts I33 reach thevertical center lines between the reel centers, and that the rockingaction is completed by the time the center line is reached (Fig. 6).Since the rocking action has the effect of moving the cutter blocksoutward from the center of the reel, it will be seen that one effect isto prevent the cutter blocks from coming into engagement as soon as theywould if they were rigidly attached to the reel. Thus the cutters do notdepend for their relative movement entirely upon their movements incircles, but they have an additional sudden movement toward one anotherwhich reaches its maximum as the center line between the reels isreached. This, along with the clamping action at I57, has the effect ofproviding a more lateral and accurate cut. This very accurate lateralcut causes all plies in a multi-ply blank to be all of the same length,rather than arranged in lapping or feathered fashion as heretofore whencutters which were afiixed to rotary members operated by a perforatingand tearing action.

The resilient pads I57 may be referred to as hedging the blades betweenthem, so that when these resilient pieces clamp the web, all of thehedged blade portions and the paper move in unison.

From the above it will be seen that the objects of the invention areaccomplished, namely accurate lateral cut-off of lengths or blanks froma multi-ply web moving at high speeds and the facility of the machine tohandle the various desired lengths to be out, without the necessity formaking any complex adjustment of the cutoff elements of the machine.

As many changes could be made in the above constructions withoutdeparting from the scope of the invention, it is intended that allmatter contained in the above description or shown in the accompanyingdrawings shall be interpreted as illustrative and not in a limitingsense.

I claim:

1. Web cut-off apparatus comprising a frame, draw rolls for drawing aweb from a supply, delivery rolls for ejecting separated lengths of Web,rotary reels on opposite sides of the web and located between said drawand delivery rolls, cutter elements on opposite sides of the web andhaving respectively rocking mounts upon the respective reels, cam meansresponsive to movement of the reels for rocking the cutter elements, thecutter elements being driven tangently to the web by rotation of thereel and being driven radially toward one another at the point oftangency by the rocking action in order to cooperate to intersect thewebs.

2. Web cut-oif apparatus comprising a frame, draw rolls for drawing aweb from a supply, delivery rolls for ejecting cut-off lengths of web,rotary reels on opposite sides of the web and between said draw anddelivery rolls, cutter elements on opposite sides of the web and havingrespectively rocking mounts upon the respective reel, cam means forrocking the cutter elements, the cutter elements being driven to a pointadjacent to opposite sides of the web by rotation of the reels and beingdriven radially toward one another by the rocking action to cooperate tointersect the web.

3. Web cut-off apparatus comprising a frame, draw rolls for drawing aweb from a supply, delivery rolls for ejecting cut-off lengths of web,rotary reels on opposite sides of the web and between said draw anddelivery rolls, cutter elements on opposite sides of the web and havingrespectively rocking mounts upon the respective reel, cam means forrocking the cutter elements, the cutter elements being driven to a pointadjacent to opposite sides of the web by rotation of the reels and beingdriven outward toward one another by the rocking action to cooperate tointersect the web, and resilient means before and behind the cuttingelements and cooperating to clamp a local region of the web at thecutting region for movement at a velocity substantially equal to thevelocity component of the cutting means in the direction of the web.

4. Web cut-oif apparatus comprising a frame,

draw rolls for drawing a web from a supply, de-

livery rolls for ejecting separated lengths of web, rotary reels onopposite sides of the web and between said draw and delivery rolls,cutter elements on opposite sides of the web and having respectivelyrocking mounts upon the respective reel, cam means for rocking thecutter elements, the cutter elements being driven to a point adjacent toopposite sides of the web by rotation of the reel and being drivenoutward toward one another by the rocking action to cooperate tointersect the webs, and resilient means before and behind the cuttingelements and cooperating to clamp a local region of the Web at thecutting region for movement substantially equal to the speed componentof the cutting means in the direction of the web, said delivery rollshaving a frictional engagement with the web of a degree adapted forejection after release by said clamping means but adapted to slip ifnecessary while said clamping means is effective during cutting.

5. Web cut-off apparatus comprising a frame, draw rolls for drawing aweb from a supply, delivery rolls for ejecting separated lengths of web,rotary reels on opposite sides of the web and between said draw anddelivery rolls, cutter elements on opposite sides of the web and havingrespectively rocking mounts upon the respective reel, cam means forrocking the cutter elements, the cutter elements being driven to a pointadjacent to opposite sides of the web by rotation of the reel and beingdriven outward toward one another by the rocking action to cooperate tointersect the webs, and resilient means before and behind the cuttingelements and cooperating to clamp a local region of the web at thecutting region for movement substantially equal to the speed componentof the cutting means in the direction of the web, said delivery rollshaving a frictional engagement with the web of a degree adapted forejection after release by said clamping means but adapted to slip ifnecessary while said clamping means is efiective during cutting, saiddraw rolls enforcing a loop of webbing ahead of the clamped web when themovement of the Web from the supply is faster than the movement of theclamped portion of the web.

6. Web cut-off apparatus comprising a frame, adjacently located,oppositely rotating reels carried by the frame, means for moving the webbetween the reels in the direction of their movement where they areadjacent to one another, stationary cams adjacent to the reels,oppositely located rocker means respectively on the reels and havingfollowers in cooperation with said cams, cutter means for the web on therockers, the cams and the followers being arranged to move the cuttermeans with an outward component with respect to the reel centers as thecutters approach one another to intersect the web.

7. Web cut-01f apparatus comprising a frame, adjacently located,oppositely rotating reels carried by the frame, means for moving the webbetween the reels in the direction of their movement where they areadjacent to one another, stationary cams on the frame and adjacent tothe reels, oppositely located rocker means respectively on the reels andhaving followers in cooperation with said cams, cooperating cutter meansfor the web on the rockers, the cams and the followers being arranged torotate the cutters outward and back with respect to the reels as thecutters intersect the web.

8. Web cut-off apparatus comprising a frame, adjacently located,oppositely rotating reels carried by the frame, means for moving the webbetween the reels in the direction of their movement where they areadjacent to one another, stationary cams on the frame and adjacent tothe reels, oppositely located rocker means respectively on the reels andhaving followers in cooperation with said cams, cooperating cutter meansfor the web on the rockers, the cams and the followers being arranged torotate the cutters outward and back with respect to the reels as thecutters intersect the web, and clamping means on the respective cuttermeans adapted to cooperate to clamp a local region of the web adjacentthe cutting means while cutting and to enforce movement of said localregion at the cutter speed along the web.

9. Web cut-01f apparatus comprising a frame, adjacently located,oppositely rotating reels carried by the frame, means for moving the web10- tween the reels in the direction of their movement adjacent to oneanother, stationary cams adjacent to the reels, oppositely locatedrocker means respectively on the reels and having followers incooperation with said cams, cooperating cutter means for the web on throckers, the cams and the followers being arranged to move the cuttermeans with an outward component with respect to the reel centers as thecutters cooperate with one another to intersect the web, and resilientclamping means on the cutter means adapted to clamp a local region ofthe web for temporary motion equal to the component of motion of thcutter means parallel to the web While cooperating to cut.

10. Web cut-off apparatus comprising a frame, adjacently located,oppositely rotating reels carried by the frame, means for moving the webbetween the reels in the direction of their movement adjacent to oneanother, stationary cams adjacent to the reels, oppositely locatedrocker means respectively on the reels and having followers incooperation with said cams, cooperating cutter means for the web on therockers, the cams and the followers being arranged to move the cuttermeans with an outward component with respect to the reel centers as thecutters cooperate With one another to intersect the web, resilientclamping means on the cutter means adapted to clamp a local region ofthe web for temporary motion equal to the component of motion of thecutter means parallel to the web while cooperating to cut, blades on onecutting means arranged to form a loose web area portion during cutting,a stripper needle mounted for rocking on the other cutting means, and acam for effecting rocking of the stripper needle so that it intersectsthe loose web area during cutting and is retracted therefrom forreleasing it after separation of thecutting elements from the web.

11 In'acut-oif machine, a rotary reeladjacent to 'a web movingtangentially thereto, a rotary cutting means on the reel and beingperipherally driven thereby to move-tangentially to the web, a

means cooperating with the cam, the cambeing shaped to force atemporarybackward and out ward swinging motion of the cutting means with respectto reel rotation as tangency is approached. 13. In gout-off machine, arotary reel adjacent 1201a tangentially moving web, a rotary cuttingmeans on the reel and being peripherally'driven thereby to swing intotangency to the web, a cam, follower means on the'rotary cutting meanscooperating with the cam, the cam being shaped to forcea temporaryoutward swinging motion of r the cutting means with respect to reelrotation as tangency is approached, and rocking stripper meansassociated with thecutting means, a second earn, a second follower onthe rocking stripper means cooperating with said second cam, said secondcam being shaped to move the stripper means relatively to the cuttingmeans.

ROBERT E. PIERCE.

